JP3594436B2

JP3594436B2 - Hydrogen storage type cooling device

Info

Publication number: JP3594436B2
Application number: JP2556397A
Authority: JP
Inventors: 勤丸橋
Original assignee: Rinnai Corp
Current assignee: Rinnai Corp
Priority date: 1997-02-07
Filing date: 1997-02-07
Publication date: 2004-12-02
Anticipated expiration: 2017-02-07
Also published as: JPH10220906A

Description

【０００１】
【発明の属する技術分野】
本発明は、水素吸蔵合金の水素の吸蔵と放出とを繰り返して行わせ、水素の放出時に生じる吸熱作用を利用して冷熱を得る水素吸蔵式冷却装置に関する。
【０００２】
【従来の技術】
水素吸蔵合金を用いた従来の水素吸蔵式冷却装置を、図１１を用いて説明する。水素吸蔵合金を用いたヒートポンプサイクルＪ１は、水素吸蔵合金Ｊ２の加熱、放熱および冷熱出力を得るためにシェル＆チューブタイプの熱交換器を用いていた。
この従来技術で示すヒートポンプサイクルＪ１は、４つのシェル＆チューブタイプの熱交換器Ｊ３〜Ｊ６を用いたもので、各熱交換器Ｊ３〜Ｊ６は水素吸蔵合金Ｊ２と熱媒体とが熱交換可能に設けられている。第１、第２熱交換器Ｊ３、Ｊ４の水素吸蔵合金Ｊ２は水素通路を介して連通し、第３、第４熱交換器Ｊ５、Ｊ６の水素吸蔵合金Ｊ２も水素通路を介して連通して設けられている。
【０００３】
作動は、第１熱交換器Ｊ３に加熱用の熱媒体を供給するとともに、第２熱交換器Ｊ４に放熱用の熱媒体を供給する。すると、第１熱交換器Ｊ３の水素が放出されて第２熱交換器Ｊ４に吸蔵される。つまり、水素駆動が行われる。
次に、第１熱交換器Ｊ３に供給していた加熱用の熱媒体を、放熱用の熱媒体に切り換えて供給するとともに、第２熱交換器Ｊ４に供給していた放熱用の熱媒体を、冷熱出力用の熱媒体に切り換えて供給する。すると、第１熱交換器Ｊ３が水素を吸蔵し、第２熱交換器Ｊ４が水素を放出する。この第２熱交換器Ｊ４が水素を放出する時、冷熱出力用の熱媒体が冷却される。つまり、冷熱出力が得られる。
そして、上記のサイクルを繰り返す。
【０００４】
一方、第２熱交換器Ｊ４から冷熱出力を得ている時は、第３熱交換器Ｊ５に加熱用の熱媒体を供給するとともに、第４熱交換器Ｊ６に放熱用の熱媒体を供給する。すると、第３熱交換器Ｊ５の水素が放出されて第４熱交換器Ｊ６に吸蔵される。つまり、第１、第２熱交換器Ｊ３、Ｊ４で冷熱出力を得ている時は、第３、第４熱交換器Ｊ５、Ｊ６で水素駆動が行われる。
次に、第３熱交換器Ｊ５に供給していた加熱用の熱媒体を、放熱用の熱媒体に切り換えて供給するとともに、第４熱交換器Ｊ６に供給していた放熱用の熱媒体を、冷熱出力用の熱媒体に切り換えて供給する。すると、第３熱交換器Ｊ５が水素を吸蔵し、第４熱交換器Ｊ６が水素を放出する。この第４熱交換器Ｊ６が水素を放出する時、冷熱出力用の熱媒体が冷却される。つまり、第１、第２熱交換器Ｊ３、Ｊ４で水素駆動が行われている時は、第３、第４熱交換器Ｊ５、Ｊ６で冷熱出力が得られる。
そして、上記のサイクルを繰り返す。
【０００５】
【発明が解決しようとする課題】
各熱交換器Ｊ３〜Ｊ６に、加熱用の熱媒体と放熱用の熱媒体、あるいは放熱用の熱媒体と冷熱出力用の熱媒体を切り換えて供給するため、従来のヒートポンプサイクルＪ１では多数の切替バルブＪ７〜Ｊ１４が必要になる。このように、多数の切替バルブＪ７〜Ｊ１４を用いると、故障確率が上昇し、耐久性の向上の妨げとなる。また、各切替バルブＪ７〜Ｊ１４は比較的高頻度で切り替わるため、作動音が目立つ不具合もあった。
【０００６】
水素吸蔵合金Ｊ２と熱媒体との熱交換を行う熱交換器Ｊ３〜Ｊ６は、水素吸蔵合金Ｊ２に水素を付与するために、一旦真空引きされた後、水素が高圧下で供給されるため、低圧と高圧の両方に耐えられるように、シェル＆チューブタイプが用いられている。しかし、シェル＆チューブタイプの熱交換器Ｊ３〜Ｊ６は、体格が大きいため、水素吸蔵合金の熱交換に関与しない部分の熱授受によるヒートロスが大きく、また水素移動時の圧力損失が大きく、結果的に冷却効率が低くなってしまう不具合があった。
【０００７】
シェル＆チューブタイプの熱交換器は、体格が大きく、上記の従来技術で示したように、連続的に冷熱出力を得るためには、ヒートポンプサイクルＪ１は最低４個の熱交換器Ｊ３〜Ｊ６を必要とするため、ヒートポンプサイクルＪ１が大型化し、結果的に水素吸蔵式冷却装置が大型化する不具合があった。
【０００８】
また、熱媒体の種類を切り換えて一方の熱交換器から他方の熱交換器へ水素の移動を行う際、両方の熱交換器に同時に異なった熱媒体を供給すると、水素移動時に生じる圧力損失によって、圧力変化にずれが生じて水素の移動が遅れ、冷却効率が低下する不具合があった。そこで、従来の水素吸蔵式冷却装置は、熱媒体の種類を切り換えて水素の移動を行う際、両方の圧力差が一定になった時点で一方の熱交換器と他方の熱交換器とを結ぶ水素通路を開いて水素の移動を促進するようにしている。
しかし、水素通路に開閉バルブを設けると、故障確率がさらに増え、耐久性が妨げられる。特に従来の装置では、熱交換器にシェル＆チューブタイプを用いていたため、上述のように水素移動時の圧力損失が大きく、圧力差が一定になるまでに時間を要し、結果的に冷却効率の改善割合が少なかった。
【０００９】
【発明の目的】
本発明は、上記の事情に鑑みてなされたもので、第１の目的は、水素吸蔵合金と熱交換を行う熱媒体の切り替えを行う切替バルブや、水素通路の開閉を行う開閉バルブが不要な長期の信頼性の高い水素吸蔵式冷却装置の提供にあり、第２の目的は、水素移動時の圧力損失を抑えるとともに、ヒートロスの小さい熱授受効率の優れた水素吸蔵式冷却装置の提供にあり、第３の目的は小型化が可能な水素吸蔵式冷却装置の提供にあり、第４の目的は、水素移動時に水素の移動を促進させて冷却効率を向上できる水素吸蔵式冷却装置の提供にある。
【００１１】
【課題を解決するための手段】
本発明の水素吸蔵式冷却装置は、上記の目的を達成するために、次の技術的手段を採用した。
（請求項１の手段）
水素吸蔵式冷却装置は、水素吸蔵合金の水素の放出時の吸熱を利用したものであって、水素吸蔵合金が封入された第１室、この第１室内と水素通路を介して連通し、水素吸蔵合金が封入された第２室を備えた複数のセルと、
前記第１室と接触可能に設けられた加熱用の熱媒体が配された加熱域を備えるとともに、前記第２室と接触可能に設けられた放熱用の熱媒体が配された第１放熱域を備える水素駆動部と、
前記第１室と接触可能に設けられた放熱用の熱媒体が配された第２放熱域を備えるとともに、前記第２室と接触可能に設けられた冷熱出力用の熱媒体が配された冷熱出力域を備える冷熱出力部と、
前記複数のセルを前記水素駆動部および前記冷熱出力部に繰り返し移動させるセル移動手段と、を備え、
前記水素駆動部において前記第１室が加熱用の熱媒体に触れ、前記第２室が放熱用の熱媒体に触れる際、前記第１室が加熱用の熱媒体に触れる接触開始時期よりも、前記第２室が放熱用の熱媒体に触れる接触開始時期が遅く設けられ、
前記冷熱出力部において前記第１室が放熱用の熱媒体に触れ、前記第２室が冷熱出力用の熱媒体に触れる際、前記第１室が放熱用の熱媒体に触れる接触開始時期よりも、前記第２室が冷熱出力用の熱媒体に触れる接触開始時期が遅く設けられるものであり、
前記第１室および前記第２室がそれぞれ放射状を呈するように前記複数のセルを配置し、
前記セル移動手段が前記複数のセルを放射状に回転駆動し、
前記加熱域と前記第２放熱域は、前記第１室の群を覆う第１容器内で区画され、
前記第１放熱域と前記冷熱出力域は、前記第２室の群を覆う第２容器内で区画され、
前記第１室に触れる熱媒体の接触開始時期と、前記第２室に触れる熱媒体の接触開始時期とのずれは、前記第１放熱域と前記冷熱出力域とを区画する前記第２容器の区画壁の位置または厚さによって設けられることを特徴とする。
【００１２】
（請求項２の手段）
請求項１の水素吸蔵式冷却装置において、
前記第２室が水素通路を介して複数に分割し、分割された一方の第２室に放熱用の熱媒体を触れさせ、分割された他方の第２室に冷熱出力用の熱媒体を触れさせ、前記他方の第２室から前記一方の第２室へ水素を移動させて冷熱出力を得るように設けるとともに、
前記一方の第２室が放熱用の熱媒体に触れ、前記他方の第２室が冷熱出力用の熱媒体に触れる際、前記一方の第２室が放熱用の熱媒体に触れる接触開始時期よりも、前記他方の第２室が冷熱出力用の熱媒体に触れる接触開始時期が遅く設けられたことを特徴とする。
【００１３】
（請求項３の手段）
請求項１または請求項２の水素吸蔵式冷却装置において、
前記第１室および前記第２室は、それぞれ偏平状を呈し、一方の面が凸状に湾曲するとともに、一方の面に対向する他方の面が凹状に湾曲して設けられたことを特徴とする。
【００１６】
【発明の作用】
（請求項１の作用）
セル移動手段が、複数のセルを、水素駆動部および冷熱出力部に繰り返し移動させる。
セルが水素駆動部に移動すると、先ず、第１室が加熱域において加熱用の熱媒体に接触する。すると、第１室が加熱を受けて水素吸蔵合金から水素が放出され、内圧が上昇する。
第１室が加熱を受けて内圧が上昇した後に、第２室が第１放熱域において放熱用の熱媒体に接触する。すると、第２室内の水素吸蔵合金が水素を吸蔵する。この時、既に第１室の内圧が上昇し、第１室内の水素吸蔵合金が水素を放出しているため、水素吸蔵合金の圧力損失による水素移動の遅れがない。
【００１７】
セルが冷熱出力部に移動すると、先ず、第１室が第２放熱域において放熱用の熱媒体に接触する。すると、第１室が放熱による温度低下を受けて水素吸蔵合金が水素を吸蔵し、内圧が下降する。
第１室が放熱されて内圧が下降した後に、第２室が冷熱出力域において冷熱出力用の熱媒体に接触する。すると、第２室内の水素吸蔵合金が水素を放出する。この時、既に第１室の内圧が下降し、第１室内の水素吸蔵合金が水素吸蔵状態となっているため、水素吸蔵合金の圧力損失による水素移動の遅れがない。
なお、この第２室の水素吸蔵合金が水素を放出する時、冷熱出力用の熱媒体が冷却され、冷熱出力が得られる。
【００１８】
【発明の効果】
本発明の水素吸蔵式冷却装置は、第１室と第２室とにそれぞれ接触する熱媒体の接触開始時期をずらすことによって、水素通路を開閉することなく、水素移動時に水素の移動を促進させることによって、水素の移動が遅れて冷却効率が低下する不具合が抑えられる。この結果、水素吸蔵式冷却装置の冷却効率が向上する。
また、第１室と第２室とを水素通路で連通したセルを複数用いているため、シェル＆チューブタイプの熱交換器に比較して、水素移動時の圧力損失を小さく抑えることができ、圧力差が一定になるまでに時間が短くて済み、結果的に従来に比較して冷却効率が改善できる。
【００１９】
本発明の水素吸蔵式冷却装置は、水素吸蔵合金に接触する熱媒体の種類を切り換えて水素吸蔵合金と熱交換を行うのではなく、セル移動手段がセルを移動することで水素吸蔵合金自体が移動して熱媒体の種類を変更しているので、従来技術のように、熱媒体の種類の切り替えを行う切替バルブが不要となる。また、水素通路を開閉する開閉弁も不要である。
このように、本発明の水素吸蔵式冷却装置は、ヒートポンプサイクルにおいて切替バルブや開閉弁が不要であるため、従来に比較して故障確率が減少し、結果的に長期の信頼性を高めることができる。
【００２０】
また、本発明の水素吸蔵式冷却装置は、水素吸蔵合金を内蔵する第１室と第２室とを水素通路で連通したセルを複数用いているため、シェル＆チューブタイプの熱交換器に比較して、熱交換に関与しない部分の熱授受が減ることでヒートロスが小さくなり、また水素移動時の圧力損失も小さくなるので、冷却効率が向上する。
【００２１】
さらに、本発明の水素吸蔵式冷却装置は、水素吸蔵合金を内蔵する複数のセルを、水素駆動部および冷熱出力部に移動することで冷熱出力を得るため、シェル＆チューブタイプの熱交換器に比較してヒートポンプサイクルの体格を小型化することができ、結果的に水素吸蔵合金を用いた水素吸蔵式冷却装置を小型化することができる。
【００２２】
【発明の実施の形態】
次に、本発明の実施の形態を、実施例および変形例に基づき説明する。
〔第１実施例の構成〕
第１実施例は、本発明の水素吸蔵式冷却装置を室内空調用の冷房装置に適用したもので、この第１実施例を図１ないし図９を用いて説明する。
【００２３】
（冷房装置１の概略説明）
本実施例の冷房装置１の概略構成を、図３を用いて説明する。この実施例では、水素吸蔵合金を用いたヒートポンプサイクル２の一例として２段式サイクルを用いた。なお、２段式サイクルとは、本発明の第２室を分割し、第１室から分割された一方の第２室に水素の移動を行い、一方の第２室から他方の第２室へ水素を移動させて１段目の冷熱出力を得、他方の第２室から第１室へ水素を移動させて２段目の冷熱出力を得るもので、詳細は後述する。
【００２４】
本実施例の適用される冷房装置１は、大別して、水素吸蔵合金を用いたヒートポンプサイクル２と、水素吸蔵合金を加熱する加熱水（加熱用の熱媒体に相当する、本実施例では水）を作り出す燃焼装置３と、水素吸蔵合金を放熱によって冷却させる放熱水（放熱用の熱媒体に相当する、本実施例では水）を冷却する放熱水冷却手段４と、水素吸蔵合金の水素放出作用によって生じた吸熱によって冷却された冷熱出力水（冷熱出力用の熱媒体に相当する、本実施例では水）で室内を空調する室内空調機５と、搭載された各電気機能部品を制御する制御装置６とから構成される。
【００２５】
なお、ヒートポンプサイクル２、燃焼装置３、放熱水冷却手段４および制御装置６は、室外機７として室外に設置されるもので、室内には室内空調機５が配置される。また、本実施例に示す冷房装置１は、１つの室外機７に対して、複数の室内空調機５が接続可能な所謂マルチエアコンである。
【００２６】
（ヒートポンプサイクル２の説明）
本実施例のヒートポンプサイクル２は、上述のように２段式サイクルを用いたもので、図１に示すように、水素吸蔵合金が封入された上段室Ｓ１（第１室に相当する）、この上段室Ｓ１内に水素通路Ｓ４を介して連通し、水素吸蔵合金が封入された中段室Ｓ２（第２室に相当する）、上段室Ｓ１内および中段室Ｓ２内に水素通路Ｓ４を介して連通し、水素吸蔵合金が封入された下段室Ｓ３（第２室に相当する）を備えたセルＳを複数用いる。なお、この実施例では、１２〜１８個のセルＳを用いた。
【００２７】
水素吸蔵合金は、水素平衡圧力が異なる３種を用いたもので、上段室Ｓ１内には同一平衡水素圧で水素平衡温度が最も高い高温度水素吸蔵合金（以下、高温合金ＨＭ）の粉末を封入し、中段室Ｓ２内には中温度水素吸蔵合金（以下、中温合金ＭＭ）の粉末を封入し、下段室Ｓ３内には同一平衡水素圧で水素平衡温度が最も低い低温度水素吸蔵合金（以下、低温合金ＬＭ）の粉末を封入したものである。
このことを図７のＰＴ冷凍サイクルを用いて説明すると、水素吸蔵合金の特性が、相対的に高温側（図示左側）にあるのが高温合金ＨＭ、低温側にあるのが低温合金ＬＭ、両者の中間にあるのが中温合金ＭＭである。
【００２８】
１つのセルＳは、ステンレスあるいは銅など、水素透過の無い金属を用いて、水素吸蔵合金を包む最中状に絞り成形したもので、真空ろう付けや溶接等の接合方法によりセル容器（上、中、下段室Ｓ１、Ｓ２、Ｓ３および水素通路Ｓ４を形成する容器）を成形し、内部に粉末状の水素吸蔵合金を充填し、真空引きを行ったのち、活性化処理を施し、水素を高圧充填して溶接により密封したものである。
【００２９】
１つのセルＳの外形は、図４に示されるもので、上、中、下段室Ｓ１、Ｓ２、Ｓ３はそれぞれ偏平状容器である板状を呈し、各室の一辺が、内部に水素通路Ｓ４が形成された棒状の連結部Ｓ５によって連結された形状を呈する。また、上、中、下段室Ｓ１、Ｓ２、Ｓ３のそれぞれは、一方の面が凸状に湾曲して設けられるとともに、対向する他方の面が凹状に湾曲して設けられている。このように、各室は、凹凸状の面を対向して設けたことにより、真空引き時の低圧下、および水素充填時の高圧下において、対向する面に引っ張り応力と圧縮応力がかかり、各室の変形が小さく抑えられ、結果的に耐圧性に優れる。
なお、凹凸の方向として、図４では側面から見て各室が湾曲するように設けたが、軸方向から見て湾曲するように設けても良いし、ドーム型など側方と軸方向の両方から見て湾曲するように設けても良い。
【００３０】
複数のセルＳは、図５に示すように、上、中、下段室Ｓ１、Ｓ２、Ｓ３が、それぞれ放射状を呈するように配置されるもので、この実施例では回転軸８の周囲に複数のセルＳの各連結部Ｓ５が束ねて固定され、複数の上段室Ｓ１の群（第１室の群に相当する）、複数の中段室Ｓ２の群（第２室の群に相当する）、複数の下段室Ｓ３の群（第２室の群に相当する）が、それぞれ放射状に配置されたものである。なお、回転軸８の周囲に固定された複数のセルＳは、図示しないセル移動手段によって回転駆動されるもので、このセル移動手段は、ゆっくりと連続的に複数のセルＳを回転させるものである（例えば、１時間に２０周ほど）。
【００３１】
一方、２段式サイクルのヒートポンプサイクル２は、図１および図２に示すように、上段室Ｓ１内の水素を強制的に下段室Ｓ３内に移動させる水素駆動部αと、下段室Ｓ３内に移動した水素を中段室Ｓ２に移動させる第１冷熱出力部βと、中段室Ｓ２内に移動した水素を上段室Ｓ１に移動させる第２冷熱出力部γとを備える。
水素駆動部αは、上段室Ｓ１と接触する加熱水（例えば８０℃ほど）が供給される加熱域α１、中段室Ｓ２と接触する昇圧水（例えば５６℃ほど）が供給される中段昇圧域α２、下段室Ｓ３と接触する放熱水（例えば２８℃ほど）が供給される下段放熱域α３（第１放熱域に相当する）を備える。
【００３２】
第１冷熱出力部βは、上段室Ｓ１と接触する昇圧水（例えば５８℃ほど）が供給される上段昇圧域β１、中段室Ｓ２と接触する放熱水（例えば２８℃ほど）が供給される中段放熱域β２、下段室Ｓ３と接触した冷熱出力水（例えば１３℃ほど）が出力される下段冷熱出力域β３を備える。
第２冷熱出力部γは、上段室Ｓ１と接触する放熱水（例えば２８℃ほど）が供給される上段放熱域γ１（第２放熱域に相当する）、中段室Ｓ２と接触する冷熱出力水（例えば１３℃ほど）が出力される中段冷熱出力域γ２（冷熱出力域に相当する）を備える。なお、第２冷熱出力部γにおいて下段室Ｓ３と接触する熱媒体の温度は不問であり、その部分を不問域γ３とする。
【００３３】
つまり、図示しないセル移動手段により、上段室Ｓ１の群は加熱域α１ →上段昇圧域β１ →上段放熱域γ１を循環するものであり、中段室Ｓ２の群は中段昇圧域α２ →中段放熱域β２ →中段冷熱出力域γ２を循環するものであり、下段室Ｓ３の群は下段放熱域α３ →下段冷熱出力域β３ →不問域γ３を循環するものである。
【００３４】
上段室Ｓ１の群は、上段容器Ｋ１（１容器に相当する）に覆われ、内部が加熱域α１、上段昇圧域β１、上段放熱域γ１に区画されている。また、中段室Ｓ２の群は、中段容器Ｋ２に覆われ、内部が中段昇圧域α２、中段放熱域β２、中段冷熱出力域γ２に区画されている。さらに、下段室Ｓ３の群は、下段容器Ｋ３に覆われ、内部が下段放熱域α３、下段冷熱出力域β３、不問域γ３に区画されている。なお、中段容器Ｋ２および下段容器Ｋ３が第２容器に相当する。
上段容器Ｋ１、中段容器Ｋ２、下段容器Ｋ３は、連続的に繋がって設けられた容器Ｋ（例えば、樹脂製の容器）で、この容器Ｋは、図６に示すように、軸方向に分割可能に設けられている。
【００３５】
この実施例のヒートポンプサイクル２は、１つのセルＳにおいて、上段室Ｓ１、中段室Ｓ２、下段室Ｓ３が熱媒体（加熱水、放熱水、昇圧水、冷熱出力水）に触れる際、ある一室に触れる熱媒体の接触開始時期と、他の一室に触れる熱媒体の接触開始時期とがずらして設けられている。
この実施例における熱媒体の接触開始時期を、図８および図９を用いて説明する。なお、図８および図９中において、実線は上段室Ｓ１内の温度および圧力変化を示し、２点鎖線は中段室Ｓ２内の温度および圧力変化を示し、破線は下段室Ｓ３内の温度および圧力変化を示す。
【００３６】
１つのセルＳが水素駆動部αへ進む際、上段室Ｓ１が加熱水に触れる接触開始時期（図中αａ）よりも、下段室Ｓ３が放熱水に触れる接触開始時期（図中αｃ）が遅く設けられている。なお、この実施例では、中段室Ｓ２が昇圧水に触れる接触開始時期（図中αｂ）は、上段室Ｓ１が加熱水に触れる接触開始時期（図中αａ）と同時に設定されている。
【００３７】
１つのセルＳが第１冷熱出力部βへ進む際、中段室Ｓ２が放熱水に触れる接触開始時期（図中βｂ）よりも、下段室Ｓ３が冷熱出力水に触れる接触開始時期（図中βｃ）が遅く設けられている。なお、この実施例では、上段室Ｓ１が昇圧水に触れる接触開始時期（図中βａ）は、中段室Ｓ２が放熱水に触れる接触開始時期（図中βｂ）と同時に設定されている。
１つのセルＳが第２冷熱出力部γへ進む際、上段室Ｓ１が放熱水に触れる接触開始時期（図中γａ）よりも、中段室Ｓ２が冷熱出力水に触れる接触開始時期（図中γｂ）が遅く設けられている。
【００３８】
上記のように、熱媒体の接触開始時期をずらす手段として、各熱媒体が供給される容器Ｋ内の区画壁の位置を調節したり、厚さを調節することにより実施している。
具体的には、図２に示すように、上段容器Ｋ１は、加熱域α１、上段昇圧域β１、上段放熱域γ１を区画する区画壁Ｋ１ａ、Ｋ１ｂ、Ｋ１ｃを備え、中段容器Ｋ２は、中段昇圧域α２、中段放熱域β２、中段冷熱出力域γ２を区画する区画壁Ｋ２ａ、Ｋ２ｂ、Ｋ２ｃを備え、下段容器Ｋ３は、下段放熱域α３、下段冷熱出力域β３、不問域γ３を区画する区画壁Ｋ３ａ、Ｋ３ｂ、Ｋ３ｃを備えている。
【００３９】
そして、水素駆動部αの進入時に下段室Ｓ３が、上段室Ｓ１、中段室Ｓ２よりも遅れて進入するように、区画壁Ｋ１ａ、Ｋ２ａよりも、区画壁Ｋ３ａがセルＳの移動方向に沿ってずれた位置に設けられている（あるいは、区画壁Ｋ３ａがセルＳの移動方向に厚く設けられている）。
また、第１冷熱出力部βの進入時に下段室Ｓ３が、上段室Ｓ１、中段室Ｓ２よりも遅れて進入するように、区画壁Ｋ１ｂ、Ｋ２ｂよりも、区画壁Ｋ３ｂがセルＳの移動方向に沿ってずれた位置に設けられている（あるいは、区画壁Ｋ３ｂがセルＳの移動方向に厚く設けられている）。
さらに、第２冷熱出力部γの進入時に中段室Ｓ２が、上段室Ｓ１、下段室Ｓ３よりも遅れて進入するように、区画壁Ｋ１ｃ、Ｋ３ｃよりも、区画壁Ｋ２ｃがセルＳの移動方向に沿ってずれた位置に設けられている（あるいは、区画壁Ｋ２ｃがセルＳの移動方向に厚く設けられている）。
【００４０】
（ヒートポンプサイクル２における上記以外の構成部品の説明）
図３に示す符号９は、上段昇圧域β１と中段昇圧域α２とに昇圧水を循環させる昇圧水循環路で、途中に設けられた昇圧水循環ポンプＰ１ ’によって昇圧水が循環する。なお、昇圧水は、加熱域α１で温度上昇した上段室Ｓ１、上段容器Ｋ１からの伝熱により温度上昇した水を用いたもので、ヒートポンプサイクル２の作動中、上段昇圧域β１の昇圧水の温度は例えば５８℃程で、中段昇圧域α２の昇圧水の温度は例えば５６℃程になる。
【００４１】
（燃焼装置３の説明）
本実施例の燃焼装置３は、燃料であるガスを燃焼して熱を発生させ、発生した熱によって加熱水を加熱するガス燃焼装置を用いたもので、ガスの燃焼を行うガスバーナ１０、このガスバーナ１０へガスの供給を行うガス量調節弁２１およびガス開閉弁２２を備えたガス供給回路１１、ガスバーナ１０へ燃焼用の空気を供給する燃焼ファン１２、ガスの燃焼熱と加熱水とを熱交換する熱交換器１３等から構成される。
そして、ガスバーナ１０のガス燃焼で得られた熱で、加熱水を例えば８０℃程に加熱し、加熱された加熱水を加熱水循環ポンプＰ１を備えた加熱水循環路１４を介して加熱域α１に供給するものである。
なお、本実施例の加熱水循環ポンプＰ１は、昇圧水循環ポンプＰ１ ’を駆動する兼用のモータによって駆動されるタンデムポンプである。このため、燃焼装置３から加熱水がヒートポンプサイクル２に供給される際は、昇圧水も循環作動するように設けられている。
【００４２】
（室内空調機５の説明）
室内空調機５は、上述のように室内に配置されるもので、内部に室内熱交換器１５、この室内熱交換器１５に供給される冷熱出力水と室内空気とを強制的に熱交換し、熱交換後の空気を室内に吹き出させるための室内ファン１６を備える。室内熱交換器１５には、下段冷熱出力域β３および中段冷熱出力域γ２から供給される冷熱出力水を循環させる冷熱出力水循環路１７が接続され、この冷熱出力水循環路１７の途中（室外機７内）には、冷熱出力水を循環させる冷熱出力水ポンプＰ２が設けられている。
【００４３】
（放熱水冷却手段４の説明）
放熱水冷却手段４は、蒸発型の冷却塔であり、この放熱水冷却手段４によって冷却された放熱水は、放熱水循環ポンプＰ３を備えた放熱水循環路１８によって下段放熱域α３、中段放熱域β２、上段放熱域γ１に供給される。
放熱水冷却手段４は、下段放熱域α３、中段放熱域β２、上段放熱域γ１を通過した放熱水を、上方から下方へ流し、流れている間に外気と熱交換して放熱するとともに、流れている間に一部蒸発させて、蒸発時に流れている放熱水から気化熱を奪い、流れている放熱水を冷却するものである。また、この放熱水冷却手段４は、図示しない放熱ファンを備え、この放熱ファンの生じる空気流によって放熱水の蒸発および冷却を促進するように設けられている。
なお、この実施例では、放熱水冷却手段４として蒸発型の冷却塔を示したが、放熱水（放熱用の熱媒体）が空気に触れずに熱交換する密閉型の冷却手段を用いても良い。
【００４４】
ここで、上記に示す加熱水循環路１４、冷熱出力水循環路１７および放熱水循環路１８は、それぞれシスターンＴ１、Ｔ２、Ｔ３を備えており、シスターンＴ１、Ｔ２、Ｔ３内の水位が所定水位以下に低下すると、それぞれに設けられた給水バルブＴ４、Ｔ５、Ｔ６が開き、給水管１９から供給される水道水をシスターンＴ１、Ｔ２、Ｔ３内に補充するように設けられている。
また、ヒートポンプサイクル２の下部にはドレンパンＰが配置され、ヒートポンプサイクル２に発生したドレン水を排水管２０から排水するように設けられている。なお、放熱水冷却手段４で溢れた水も排水管２０から排水するように設けられている。
【００４５】
（制御装置６の説明）
制御装置６は、室内空調機５に設けられたコントローラ（図示しない）からの操作指示や、複数設けられた各センサの入力信号に応じて、上述の加熱水循環ポンプＰ１（昇圧水循環ポンプＰ１ ’）、冷熱出力水ポンプＰ２、放熱水循環ポンプＰ３、給水バルブＴ４、Ｔ５、Ｔ６、放熱水冷却手段４の放熱ファンなどの電気機能部品、および燃焼装置３の電気機能部品（燃焼ファン１２、ガス量調節弁２１、ガス開閉弁２２、図示しない点火装置等）を制御するとともに、室内空調機５に室内ファン１６の作動指示を与えるものである。
【００４６】
（冷房運転の作動説明）
上記の冷房装置１による冷房運転の作動を、図７のＰＴ冷凍サイクル線図、図８の温度変化を示すグラフ、図９の圧力変化を示すグラフを参照して説明する。冷房運転が室内空調機５のコントローラによって指示されると、制御装置６によって、燃焼装置３、セル移動手段、放熱ファンおよび加熱水循環ポンプＰ１（昇圧水循環ポンプＰ１ ’）、冷熱出力水ポンプＰ２、放熱水循環ポンプＰ３が作動するとともに、冷房が指示された室内空調機５の室内ファン１６をＯＮする。
【００４７】
セル移動手段によって、複数のセルＳがゆっくりと連続的に回転移動する。これによって、複数のセルＳが、水素駆動部α→第１冷熱出力部β→第２冷熱出力部γの順で移動する。
つまり、各上段室Ｓ１が加熱域α１ →上段昇圧域β１ →上段放熱域γ１の順で移動し、各中段室Ｓ２が中段昇圧域α２ →中段放熱域β２ →中段冷熱出力域γ２の順で移動し、各下段室Ｓ３が下段放熱域α３ →下段冷熱出力域β３ →不問域γ３の順で移動する。
【００４８】
水素駆動部αへ進入するセルＳは、先ず、上段室Ｓ１および中段室Ｓ２が加熱水および昇圧水に触れる（図８のαａ、αｂ）。上段室Ｓ１が加熱水（８０℃）に触れることにより、高温合金ＨＭは水素を放出し、内圧が上昇する（図９のαａ）。また、中段室Ｓ２が昇圧水に触れることにより、中温合金ＭＭが水素を吸蔵しない圧力に上昇する（図９のαｂ）。
上段室Ｓ１および中段室Ｓ２の内圧が上昇した後に、下段室Ｓ３が放熱水（２８℃）に接触することにより（図８のαｃ）、低温合金ＬＭが水素の吸蔵を開始する（図９のαｃ）。この時、既に上段室Ｓ１の内圧が上昇し、高温合金ＨＭは水素を放出しているため、高温合金ＨＭの圧力損失による水素移動の遅れによる影響を受けることなく、低温合金ＬＭは水素を吸蔵する。
【００４９】
このように、上段室Ｓ１が加熱域α１で加熱水に触れ、中段室Ｓ２が中段昇圧域α２で昇圧水に触れ、下段室Ｓ３が下段放熱域α３の放熱水に触れることにより、上段室Ｓ１内が８０℃：１．０ＭＰａ、中段室Ｓ２内が５６℃：１．０ＭＰａ、下段室Ｓ３内が２８℃：０．９ＭＰａとなり、上段室Ｓ１の高温合金ＨＭが水素を放出し（図７の▲１▼）、下段室Ｓ３の低温合金ＬＭが水素を吸蔵する（図７の▲２▼）。なお、中段室Ｓ２は昇圧水によって加熱されて内圧が高く、中温合金ＭＭは水素の吸蔵は行わない。
そして、水素駆動部αを通過したセルＳは、その後第１冷熱出力部βへ移動する。
【００５０】
第１冷熱出力部βへ進入するセルＳは、先ず、上段室Ｓ１および中段室Ｓ２が昇圧水および放熱水に触れる（図８のβａ、βｂ）。上段室Ｓ１が昇圧水（５８℃）に触れることにより、高温合金ＨＭが水素を吸蔵しない圧力に上昇する（図９のβａ）。中段室Ｓ２が放熱水（２８℃）に触れることにより、中温合金ＭＭの水素吸蔵作用によって、内圧が下降する（図９のβｂ）。
中段室Ｓ２の内圧が下降した後に、下段室Ｓ３が冷熱出力水に接触することにより（図８のβｃ）、低温合金ＬＭの水素の放出が促進される（図９のβｃ）。つまり、下段室Ｓ３が冷熱出力水に接触した時は、既に中段室Ｓ２の内圧が降下しているため、中温合金ＭＭの圧力損失による水素移動の遅れの影響を受けることなく、低温合金ＬＭは水素を放出する。
【００５１】
このように、上段室Ｓ１が上段昇圧域β１で昇圧水に触れ、中段室Ｓ２が中段昇圧域β２で放熱水に触れ、下段室Ｓ３が下段冷熱出力域β３の冷熱出力水に触れることにより、上段室Ｓ１内が５８℃：０．５ＭＰａ、中段室Ｓ２内が２８℃：０．４ＭＰａ、下段室Ｓ３内が１３℃：０．５ＭＰａとなり、下段室Ｓ３の低温合金ＬＭが水素を放出し（図７の▲３▼）、中段室Ｓ２の中温合金ＭＭが水素を吸蔵する（図７の▲４▼）。下段室Ｓ３の低温合金ＬＭが水素を放出する際、吸熱作用が発生し、下段室Ｓ３に触れる冷熱出力水から熱を奪う。この結果、下段冷熱出力域β３内の冷熱出力水の温度が低下する（例えば、１３℃）。なお、上段室Ｓ１は昇圧水によって加熱されて内圧が高く、高温合金ＨＭは水素の吸蔵は行わない。
そして、第１冷熱出力部βを通過したセルＳは、その後第２冷熱出力部γへ移動する。
【００５２】
第２冷熱出力部γへ進入するセルＳは、先ず、上段室Ｓ１が放熱水に触れる（図８のγａ）。上段室Ｓ１が放熱水（２８℃）に触れることにより、高温合金ＨＭの水素吸蔵作用によって、内圧が下降する（図９のγａ）。
上段室Ｓ１の内圧が下降した後に、中段室Ｓ２が冷熱出力水に接触することにより（図８のγｂ）、中温合金ＭＭの水素の放出が促進される（図９のγｂ）。つまり、中段室Ｓ２が冷熱出力水に接触した時は、既に上段室Ｓ１の内圧が降下しているため、高温合金ＨＭの圧力損失による水素移動の遅れによる影響を受けることなく、中温合金ＭＭは水素を放出する。
【００５３】
このように、上段室Ｓ１が上段放熱域γ１で放熱水に触れることにより、上段室Ｓ１内が２８℃：０．１ＭＰａ、中段室Ｓ２内が１３℃：０．２ＭＰａ、下段室Ｓ３内は不問状態となり、中段室Ｓ２の中温合金ＭＭが水素を放出し（図７の▲５▼）、上段室Ｓ１の高温合金ＨＭが水素を吸蔵する（図７の▲６▼）。中段室Ｓ２の中温合金ＭＭが水素を放出する際、吸熱作用が発生し、中段室Ｓ２に触れる冷熱出力水から熱を奪う。この結果、中段冷熱出力域γ２内の冷熱出力水の温度が低下する（例えば、１３℃）。なお、下段室Ｓ３の温度は無関係で、下段室Ｓ３の低温合金ＬＭは水素の吸蔵は行わない。
そして、第２冷熱出力部γを通過したセルＳは、その後水素駆動部αへ移動する。
【００５４】
なお、ヒートポンプサイクル２の下段冷熱出力域β３および中段冷熱出力域γ２で熱を奪われた低温の冷熱出力水は、冷熱出力水循環路１７を介して室内空調機５の室内熱交換器１５に供給されて、室内に吹き出される空気と熱交換されて室内を冷房する。
【００５５】
〔実施例の効果〕
上記の作動で示したように、本実施例の冷房装置１は、１つのセルＳにおいて、上段室Ｓ1 、中段室Ｓ2 、下段室Ｓ3 が熱媒体（加熱水、放熱水、昇圧水、冷熱出力水）に触れる際、ある一室に触れる熱媒体の接触開始時期と、他の一室に触れる熱媒体の接触開始時期とをずらしたことによって、水素通路Ｓ4 を開閉することなく、水素移動時に水素の移動を促進させることによって、水素の移動が遅れて冷却効率が低下する不具合が抑えられ、冷房装置１の冷却効率を向上できる。
また、上段室Ｓ1 、中段室Ｓ2 、下段室Ｓ3 を水素通路Ｓ4 で連通したセルＳを複数用いているため、シェル＆チューブタイプの熱交換器に比較して、水素移動時の圧力損失を小さく抑えることができ、圧力差が一定になるまでに時間（つまり、ずらす時間）が短くて済み、冷却効率が改善できる。
【００５６】
本実施例の冷房装置１は、従来技術のように水素吸蔵合金に接触する熱媒体の種類を切り換えて水素吸蔵合金と熱交換を行うのではなく、セル移動手段が複数のセルＳを移動することで水素吸蔵合金自体が移動して熱媒体の種類（加熱水、放熱水、昇圧水、冷熱出力水）を変更しているので、ヒートポンプサイクル２において熱媒体の種類を切り替える切替バルブが不要となる。また、上段室Ｓ１、中段室Ｓ２、下段室Ｓ３はいずれも水素通路Ｓ４によって連通しているのみであるため、水素通路Ｓ４の開閉バルブも必要ない。
このように、本実施例の冷房装置１は、ヒートポンプサイクル２において熱媒体を頻繁に切り替える切替バルブが不要であるため、従来に比較して故障確率が減少し、結果的に長期の信頼性が向上する。
【００５７】
本発明を適用した冷房装置１は、水素吸蔵合金を内蔵する上段室Ｓ１、中段室Ｓ２、下段室Ｓ３を水素通路Ｓ４で連通したセルＳを複数用いているため、シェル＆チューブタイプの熱交換器に比較して、熱交換に関与しない部分の熱授受が減ってヒートロスを小さくできるとともに、水素移動時の圧力損失が小さく抑えられ、結果的にヒートポンプサイクル２の冷却効率が向上し、冷房効率が向上する。
【００５８】
本発明を適用した冷房装置１のヒートポンプサイクル２は、従来のようなシェル＆チューブタイプの熱交換器を複数用いるのではなく、複数のセルＳを集合し、１つの容器Ｋ内に収容したものである。このため、シェル＆チューブタイプの熱交換器を複数用いた従来のヒートポンプサイクルに比較して、本実施例のヒートポンプサイクル２の体格を大変小型化することができ、結果的に冷房装置１の室外機７を小型化できる。
【００５９】
〔第２実施例〕
次に、本発明の水素吸蔵式冷却装置を冷暖房装置に適用した第２実施例を示す。なお、図１０は本発明を適用した冷暖房装置の概略構成図である。
本実施例の冷暖房装置３０は、上記の実施例で示した冷房運転の実施に加え、暖房運転時に、燃焼装置３で加熱された加熱水を室内空調機５の室内熱交換器１５に導いて室内暖房を行うもので、第１実施例で示した加熱水循環路１４と冷熱出力水循環路１７とを接続し、その接続部分に流路切替用の３つの切替バルブＶ１、Ｖ２、Ｖ３（冷房と暖房の切替バルブ）を設けたものである。
なお、室内空調機５の他に、床暖房マット、浴室乾燥機などに接続し、加熱水の供給によって床暖房、浴室暖房などを行うように設けても良い。
【００６０】
〔変形例〕
上記の実施例では、セルＳの各室が次の熱媒体域に進入する毎に、熱媒体の接触開始時期をずらした例を示したが、一部のみずらしても良い。つまり、例えば、水素駆動部αのみをずらしたり、第１冷熱出力部βのみをずらしたり、第２冷熱出力部γのみをずらすなどしても良い。
【００６１】
上記の第１、第２実施例では、説明を容易化するために、図面の上下に応じて上段室Ｓ１、中段室Ｓ２、下段室Ｓ３とした例を示したが、セルＳの回転方向を横に向けたり、反転させるなど、他の向きに配置しても良い。また、上段室Ｓ１、中段室Ｓ２、下段室Ｓ３の配置を入れ換えても良い。さらに、セルＳの移動方向を逆にしても良い。このような場合は、勿論、各室に接触する各熱媒体の配置位置もヒートポンプサイクルが成り立つように入れ換える。
【００６２】
上記の実施例では、昇圧用の熱媒体として、加熱域α１で温度上昇した上段室Ｓ１を冷却して温度上昇した熱媒体（実施例中では昇圧水）を用いた例を示したが、加熱手段（例えば、燃焼装置による昇温、電気ヒータによる昇温、排熱を利用した昇温など）によって昇温した熱媒体を用いても良い。
上記の実施例では、ヒートポンプサイクル２の一例として、２段式サイクルを用いた例を示したが、１段式サイクルに用いても良いし、第２室を３つ以上分割して３段式以上のサイクルとして用いても良い。
【００６３】
上記の実施例では、１つの室外機７に複数の室内空調機５が接続可能なマルチエアコンを示したが、１つの室外機７に１つの室内空調機５が接続されるエアコンに本発明を適用しても良い。
上記の実施例では、ヒートポンプサイクル２によって得られた冷熱出力用の熱媒体（実施例中では冷熱水）で室内を冷房する例を示したが、冷熱出力用の熱媒体で冷蔵運転や冷凍運転に用いるなど、本発明を他の冷却装置として用いても良い。
【００６４】
上記の実施例では、１つのヒートポンプユニット（１つの容器Ｋ内に複数のセルＳを収納したユニット）を用いた例を示したが、複数のヒートポンプユニットを搭載して冷却能力を増大させ、ビル用空調システムなど大きな冷却能力が要求される冷却装置に用いても良い。
【００６５】
上記の実施例では、加熱用の熱媒体（実施例中では加熱水）を加熱する加熱手段として、ガスを燃焼するガス燃焼装置を用いたが、石油を燃焼する石油燃焼装置など、他の燃焼装置を用いても良いし、内燃機関の排熱によって加熱用の熱媒体を加熱する加熱手段、ボイラーによる蒸気、電気ヒータを用いた加熱手段など、他の加熱手段を用いても良い。なお、内燃機関の排熱を利用する際は、車両用に用いることもできる。
【００６６】
上記の実施例では、各熱媒体の一例として、水道水を用いたが、不凍液やオイルなど他の液体の熱媒体を用いても良し、空気など気体の熱媒体を用いても良い。
上記の実施例では、複数のセルＳをセル移動手段によって連続的に回転させた例を示したが、セルＳを間欠的に回転移動させても良い。
【図面の簡単な説明】
【図１】ヒートポンプサイクルの作動説明図である（第１実施例）。
【図２】セルの集合体を収納する容器各部の断面図である（第１実施例）。
【図３】冷房装置の概略構成図である（第１実施例）。
【図４】セルの斜視図である（第１実施例）。
【図５】複数のセルの配置状態を示す斜視図である（第１実施例）。
【図６】容器の斜視図である（第１実施例）。
【図７】ＰＴ冷凍サイクル線図である（第１実施例）。
【図８】各室内の温度変化を示すグラフである（第１実施例）。
【図９】各室内の圧力変化を示すグラフである（第１実施例）。
【図１０】冷暖房装置の概略構成図である（第２実施例）。
【図１１】冷房装置の概略構成図である（従来例）。
【符号の説明】
ＨＭ高温合金（水素吸蔵合金）
ＭＭ中温合金（水素吸蔵合金）
ＬＭ低温合金（水素吸蔵合金）
Ｓセル
Ｓ１上段室（第１室）
Ｓ２中段室（第２室）
Ｓ３下段室（第２室）
Ｓ４水素通路
α 水素駆動部
α１加熱域
α３下段放熱域（第１放熱域）
γ 第２冷熱出力部（冷熱出力部）
γ１上段放熱域（第２放熱域）
γ２中段冷熱出力域（冷熱出力域）
Ｋ１上段容器（第１容器）
Ｋ２中段容器（第２容器）
Ｋ３下段容器（第２容器）[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a hydrogen-absorbing cooling device that repeatedly absorbs and releases hydrogen of a hydrogen-absorbing alloy and obtains cold heat by utilizing an endothermic effect generated at the time of releasing hydrogen.
[0002]
[Prior art]
A conventional hydrogen storage type cooling device using a hydrogen storage alloy will be described with reference to FIG. In the heat pump cycle J1 using the hydrogen storage alloy, a shell-and-tube type heat exchanger was used in order to obtain heating, heat radiation and cooling output of the hydrogen storage alloy J2.
The heat pump cycle J1 shown in this prior art uses four shell-and-tube type heat exchangers J3 to J6. Each of the heat exchangers J3 to J6 enables heat exchange between the hydrogen storage alloy J2 and the heat medium. Is provided. The hydrogen storage alloy J2 of the first and second heat exchangers J3 and J4 communicates via a hydrogen passage, and the hydrogen storage alloy J2 of the third and fourth heat exchangers J5 and J6 also communicates via a hydrogen passage. Is provided.
[0003]
In operation, a heat medium for heating is supplied to the first heat exchanger J3, and a heat medium for heat radiation is supplied to the second heat exchanger J4. Then, hydrogen in the first heat exchanger J3 is released and occluded in the second heat exchanger J4. That is, hydrogen driving is performed.
Next, the heat medium for heating supplied to the first heat exchanger J3 is switched to a heat medium for heat radiation and supplied, and the heat medium for heat radiation supplied to the second heat exchanger J4 is supplied to the second heat exchanger J4. , And the heat medium for cooling output is switched and supplied. Then, the first heat exchanger J3 stores hydrogen, and the second heat exchanger J4 releases hydrogen. When the second heat exchanger J4 emits hydrogen, the heat medium for cold output is cooled. That is, a cooling output is obtained.
Then, the above cycle is repeated.
[0004]
On the other hand, when a cold heat output is obtained from the second heat exchanger J4, a heat medium for heating is supplied to the third heat exchanger J5 and a heat medium for heat radiation is supplied to the fourth heat exchanger J6. . Then, the hydrogen in the third heat exchanger J5 is released and stored in the fourth heat exchanger J6. In other words, when the first and second heat exchangers J3 and J4 are obtaining the cold heat output, the third and fourth heat exchangers J5 and J6 are driven by hydrogen.
Next, the heat medium for heating supplied to the third heat exchanger J5 is switched and supplied to the heat medium for heat radiation, and the heat medium for heat radiation supplied to the fourth heat exchanger J6 is supplied to the third heat exchanger J6. , And the heat medium for cooling output is switched and supplied. Then, the third heat exchanger J5 absorbs hydrogen, and the fourth heat exchanger J6 releases hydrogen. When the fourth heat exchanger J6 emits hydrogen, the heat medium for cold output is cooled. That is, when the first and second heat exchangers J3 and J4 are driven by hydrogen, the third and fourth heat exchangers J5 and J6 can obtain a cooling output.
Then, the above cycle is repeated.
[0005]
[Problems to be solved by the invention]
In order to supply a heat medium for heating and a heat medium for heat dissipation, or a heat medium for heat dissipation and a heat medium for cold heat output to each of the heat exchangers J3 to J6, a large number of switching operations are performed in the conventional heat pump cycle J1. Valves J7 to J14 are required. As described above, when a large number of switching valves J7 to J14 are used, the failure probability increases, which hinders improvement in durability. Further, since the switching valves J7 to J14 are switched relatively frequently, there is a problem that the operation noise is conspicuous.
[0006]
Since the heat exchangers J3 to J6 that perform heat exchange between the hydrogen storage alloy J2 and the heat medium are once evacuated to supply hydrogen to the hydrogen storage alloy J2, hydrogen is supplied under high pressure. Shell & tube type is used to withstand both low pressure and high pressure. However, since the shell and tube type heat exchangers J3 to J6 are large in size, heat loss due to heat exchange in a portion not involved in heat exchange of the hydrogen storage alloy is large, and pressure loss during hydrogen transfer is large. However, there was a problem that the cooling efficiency was lowered.
[0007]
The heat exchanger of the shell & tube type has a large size, and as shown in the above-mentioned prior art, in order to continuously obtain a cooling output, the heat pump cycle J1 requires at least four heat exchangers J3 to J6. As a result, the heat pump cycle J1 becomes large, and as a result, there is a problem that the hydrogen storage type cooling device becomes large.
[0008]
When hydrogen is transferred from one heat exchanger to the other by switching the type of heat medium, supplying a different heat medium to both heat exchangers simultaneously causes a pressure loss caused during hydrogen transfer. In addition, there has been a problem that a shift in pressure change occurs, delaying the movement of hydrogen, and lowering cooling efficiency. Therefore, the conventional hydrogen storage type cooling device connects one heat exchanger and the other heat exchanger when the pressure difference between the two becomes constant when switching the type of the heat medium to transfer hydrogen. The hydrogen passage is opened to promote the movement of hydrogen.
However, providing an on-off valve in the hydrogen passage further increases the probability of failure and hinders durability. Particularly, in the conventional apparatus, since the shell and tube type is used for the heat exchanger, the pressure loss during the transfer of hydrogen is large as described above, and it takes time until the pressure difference becomes constant, resulting in cooling efficiency. The rate of improvement was small.
[0009]
[Object of the invention]
The present invention has been made in view of the above circumstances, and a first object is that a switching valve for switching a heat medium for performing heat exchange with a hydrogen storage alloy and an opening and closing valve for opening and closing a hydrogen passage are unnecessary. The second object is to provide a long-term reliable hydrogen-absorbing cooling device. The second object is to provide a hydrogen-absorbing cooling device that suppresses pressure loss during hydrogen transfer and has excellent heat transfer efficiency with small heat loss. A third object is to provide a hydrogen storage type cooling device that can be reduced in size, and a fourth object is to provide a hydrogen storage type cooling device that can improve the cooling efficiency by promoting the movement of hydrogen during hydrogen transfer. is there.
[0011]
[ Means for Solving the Problems ]
The hydrogen storage cooling device of the present invention employs the following technical means to achieve the above object.
(Means of claim 1 )
The hydrogen-absorbing cooling device utilizes heat absorption of the hydrogen-absorbing alloy at the time of release of hydrogen. The hydrogen-absorbing cooling device communicates with the first chamber in which the hydrogen-absorbing alloy is sealed, and communicates with the first chamber through a hydrogen passage. A plurality of cells having a second chamber in which the storage alloy is sealed;
A first heat radiating area provided with a heat medium for heating provided in contact with the first chamber and provided with a heat medium for heat radiating provided in contact with the second chamber; A hydrogen drive unit comprising:
A second heat radiation area provided with a heat medium for heat radiation provided so as to be capable of contacting the first chamber, and a cold heat provided with a heat medium for heat output provided so as to be able to contact the second chamber; A cooling output unit having an output area,
Cell moving means for repeatedly moving the plurality of cells to the hydrogen drive unit and the cold heat output unit,
When the first chamber contacts the heating medium for heating in the hydrogen driving unit, and the second chamber contacts the heating medium for heat radiation, the first chamber comes into contact with the heating medium for heating, more than the contact start time. The contact start timing at which the second chamber comes into contact with the heat medium for heat radiation is provided late,
When the first chamber is in contact with the heat medium for heat dissipation in the cold heat output section and the second chamber is in contact with the heat medium for heat output, the first chamber is in contact with the heat medium for heat dissipation, which is shorter than the contact start time. the second chamber is shall have provided slow contact start time to touch the heat medium for cold output,
The plurality of cells are arranged such that the first chamber and the second chamber each have a radial shape,
The cell moving means radially drives the plurality of cells,
The heating area and the second heat radiation area are partitioned in a first container that covers the group of the first chamber,
The first heat radiation area and the cold heat output area are partitioned in a second container covering the group of the second chamber;
The difference between the contact start time of the heat medium that touches the first chamber and the contact start time of the heat medium that touches the second chamber is the difference between the first heat radiation area and the cold heat output area. It is characterized by being provided depending on the position or thickness of the partition wall .
[0012]
(Means of Claim 2 )
The hydrogen storage type cooling device according to claim 1 ,
The second chamber is divided into a plurality of sections through a hydrogen passage, one of the divided second chambers is brought into contact with a heat medium for heat radiation, and the other of the divided second chambers is contacted with a heat medium for cold heat output. And hydrogen is transferred from the other second chamber to the one second chamber so as to obtain a cooling output,
When the one second chamber is in contact with the heat medium for heat dissipation and the other second chamber is in contact with the heat medium for cold heat output, the contact start time when the one second chamber is in contact with the heat medium for heat dissipation is Also, the contact start time of the other second chamber in contact with the heat medium for cold heat output is provided later.
[0013]
(Means of Claim 3 )
The hydrogen-absorbing cooling device according to claim 1 or 2 ,
The first chamber and the second chamber each have a flat shape, and one surface is curved in a convex shape, and the other surface facing one surface is provided in a concave shape. I do.
[0016]
Effect of the Invention
(Operation of Claim 1 )
The cell moving means repeatedly moves the plurality of cells to the hydrogen driving unit and the cold heat output unit.
When the cell moves to the hydrogen drive unit, first, the first chamber comes into contact with a heating medium for heating in the heating zone. Then, the first chamber is heated, hydrogen is released from the hydrogen storage alloy, and the internal pressure rises.
After the first chamber is heated and the internal pressure is increased, the second chamber contacts the heat medium for heat radiation in the first heat radiation area. Then, the hydrogen storage alloy in the second chamber stores hydrogen. At this time, since the internal pressure of the first chamber has already increased and the hydrogen storage alloy in the first chamber has released hydrogen, there is no delay in hydrogen transfer due to the pressure loss of the hydrogen storage alloy.
[0017]
When the cell moves to the cold output section, first, the first chamber contacts the heat medium for heat dissipation in the second heat dissipation area. Then, the first chamber receives a temperature decrease due to heat radiation, and the hydrogen storage alloy stores hydrogen, and the internal pressure decreases.
After the first chamber is dissipated and the internal pressure drops, the second chamber contacts the heat medium for cold output in the cold output area. Then, the hydrogen storage alloy in the second chamber releases hydrogen. At this time, the internal pressure of the first chamber has already dropped, and the hydrogen storage alloy in the first chamber is in the hydrogen storage state, so that there is no delay in the movement of hydrogen due to the pressure loss of the hydrogen storage alloy.
When the hydrogen storage alloy in the second chamber releases hydrogen, the heat medium for cooling output is cooled, and a cooling output is obtained.
[0018]
【The invention's effect】
ADVANTAGE OF THE INVENTION The hydrogen storage type cooling apparatus of this invention accelerates the movement of hydrogen at the time of hydrogen transfer by opening and closing a hydrogen passage by shifting the contact start time of the heat medium which respectively contacts a 1st chamber and a 2nd chamber . This suppresses the problem that the movement of hydrogen is delayed and the cooling efficiency is reduced. As a result, the cooling efficiency of the hydrogen storage type cooling device is improved.
Further, since a plurality of cells in which the first chamber and the second chamber communicate with each other through the hydrogen passage are used, the pressure loss at the time of hydrogen transfer can be suppressed as compared with the shell and tube type heat exchanger, The time required until the pressure difference becomes constant can be shortened, and as a result, the cooling efficiency can be improved as compared with the conventional case.
[0019]
The hydrogen storage type cooling device of the present invention does not exchange heat with the hydrogen storage alloy by switching the type of the heat medium in contact with the hydrogen storage alloy, but the hydrogen storage alloy itself is moved by the cell moving means to move the cell. Since the type of the heat medium is changed by moving, the switching valve for switching the type of the heat medium as in the related art is not required. Further, an on-off valve for opening and closing the hydrogen passage is not required.
As described above, the hydrogen storage cooling device of the present invention does not require a switching valve or an opening / closing valve in the heat pump cycle, so that the failure probability is reduced as compared with the related art, and as a result, long-term reliability can be improved. it can.
[0020]
In addition, the hydrogen-absorbing cooling device of the present invention uses a plurality of cells in which the first and second chambers containing the hydrogen-absorbing alloy are communicated with each other through a hydrogen passage, and thus is compared with a shell-and-tube type heat exchanger. As a result, heat loss in a portion not involved in heat exchange is reduced, so that heat loss is reduced, and pressure loss during hydrogen transfer is also reduced, so that cooling efficiency is improved.
[0021]
Further, the hydrogen storage type cooling device of the present invention is provided with a shell and tube type heat exchanger for obtaining a cold output by moving a plurality of cells containing a hydrogen storage alloy to a hydrogen driving section and a cold output section. In comparison, the physique of the heat pump cycle can be reduced in size, and as a result, the hydrogen storage cooling device using the hydrogen storage alloy can be reduced in size.
[0022]
BEST MODE FOR CARRYING OUT THE INVENTION
Next, embodiments of the present invention will be described based on examples and modifications.
[Configuration of First Embodiment]
In the first embodiment, the hydrogen storage type cooling device of the present invention is applied to a cooling device for indoor air conditioning. The first embodiment will be described with reference to FIGS.
[0023]
(Schematic description of cooling device 1)
A schematic configuration of the cooling device 1 of the present embodiment will be described with reference to FIG. In this example, a two-stage cycle was used as an example of the heat pump cycle 2 using a hydrogen storage alloy. In the two-stage cycle, the second chamber of the present invention is divided, and hydrogen is transferred from the first chamber to one of the divided second chambers, and from one second chamber to the other second chamber. The first stage of cold output is obtained by moving hydrogen, and the second stage of cold output is obtained by transferring hydrogen from the other second chamber to the first chamber, which will be described in detail later.
[0024]
The cooling device 1 to which the present embodiment is applied is roughly classified into a heat pump cycle 2 using a hydrogen storage alloy, and heating water for heating the hydrogen storage alloy (corresponding to a heating medium for heating, water in this embodiment). , A cooling water device 4 for cooling facility water for cooling the hydrogen storage alloy by heat radiation (corresponding to a heat medium for heat dissipation, water in this embodiment), and a hydrogen releasing function of the hydrogen storage alloy. The indoor air conditioner 5 air-conditions the room with cold output water (corresponding to a heat medium for cold output, in this embodiment, water) cooled by the heat absorption generated by the heat absorption, and control for controlling each mounted electric functional component. And an apparatus 6.
[0025]
The heat pump cycle 2, the combustion device 3, the facility water cooling means 4 and the control device 6 are installed outdoors as an outdoor unit 7, and an indoor air conditioner 5 is arranged indoors. The cooling device 1 shown in the present embodiment is a so-called multi air conditioner in which a plurality of indoor air conditioners 5 can be connected to one outdoor unit 7.
[0026]
(Explanation of heat pump cycle 2)
The heat pump cycle 2 of the present embodiment uses a two-stage cycle as described above, and as shown in FIG. 1, an upper chamber S1 (corresponding to a first chamber) in which a hydrogen storage alloy is sealed. The middle chamber S2 (corresponding to the second chamber) in which the hydrogen storage alloy is sealed communicates with the upper chamber S1 via the hydrogen passage S4, and the hydrogen chamber S2 and the middle chamber S2 via the hydrogen passage S4. Then, a plurality of cells S having a lower chamber S3 (corresponding to the second chamber) in which the hydrogen storage alloy is sealed are used. In this example, 12 to 18 cells S were used.
[0027]
The hydrogen storage alloy uses three kinds of hydrogen equilibrium pressures different from each other. In the upper chamber S1, powder of a high-temperature hydrogen storage alloy (hereinafter, high-temperature alloy HM) having the same hydrogen equilibrium pressure and the highest hydrogen equilibrium temperature is placed. The middle stage chamber S2 is filled with a powder of a medium temperature hydrogen storage alloy (hereinafter referred to as a middle temperature alloy MM), and the lower room S3 is filled with a low temperature hydrogen storage alloy having the same hydrogen pressure and the lowest hydrogen equilibrium temperature. Hereinafter, the powder of the low temperature alloy LM) is sealed.
This will be described with reference to the PT refrigeration cycle shown in FIG. 7. The properties of the hydrogen storage alloy are relatively high on the high temperature side (left side in the figure), high temperature alloy HM, and low on the low temperature side. Intermediate temperature is the intermediate temperature alloy MM.
[0028]
One cell S is made of a metal having no hydrogen permeation, such as stainless steel or copper, and is formed by drawing in the middle of enclosing the hydrogen storage alloy. The cell container is formed by a joining method such as vacuum brazing or welding. Containers forming the middle and lower chambers S1, S2, S3 and the hydrogen passage S4) are formed, and the inside thereof is filled with a powdery hydrogen storage alloy, evacuated, activated, and subjected to high pressure hydrogen. Filled and sealed by welding.
[0029]
The outer shape of one cell S is shown in FIG. 4. The upper, middle, and lower chambers S1, S2, and S3 each have a plate shape as a flat container, and one side of each chamber has a hydrogen passage S4 therein. Have a shape connected by a rod-shaped connecting portion S5 formed with. Each of the upper, middle, and lower chambers S1, S2, and S3 is provided with one surface curved in a convex shape and the other opposing surface curved in a concave shape. As described above, since each chamber is provided with the concavo-convex surfaces opposed to each other, a tensile stress and a compressive stress are applied to the opposed surfaces under a low pressure during evacuation and a high pressure during hydrogen filling. The deformation of the chamber is kept small, resulting in excellent pressure resistance.
In FIG. 4, the direction of the unevenness is such that each chamber is curved when viewed from the side, but may be provided so as to be curved when viewed from the axial direction. It may be provided so as to be curved as viewed from above.
[0030]
As shown in FIG. 5, the plurality of cells S are arranged such that the upper, middle, and lower chambers S1, S2, and S3 each have a radial shape. In this embodiment, a plurality of cells S are arranged around the rotation shaft 8. Each connecting portion S5 of the cells S is bundled and fixed, and a plurality of groups of upper chambers S1 (corresponding to a group of first chambers), a plurality of groups of middle chambers S2 (corresponding to a group of second chambers), a plurality of The lower group S3 (corresponding to the group of the second chamber) is radially arranged. The plurality of cells S fixed around the rotation shaft 8 are driven to rotate by cell moving means (not shown). The cell moving means slowly and continuously rotates the plurality of cells S. There are (for example, about 20 laps per hour).
[0031]
On the other hand, as shown in FIG. 1 and FIG. 2, the heat pump cycle 2 of the two-stage cycle includes a hydrogen driving unit α for forcibly moving hydrogen in the upper chamber S1 into the lower chamber S3, and a hydrogen driving unit α in the lower chamber S3. A first cold output unit β for moving the moved hydrogen to the middle chamber S2 and a second cold output unit γ for moving the hydrogen moved to the middle chamber S2 to the upper chamber S1 are provided.
The hydrogen drive unit α includes a heating zone α1 to which heated water (for example, about 80 ° C.) that comes into contact with the upper chamber S1 is supplied, and a middle boosted area α2 to which pressurized water (for example, about 56 ° C.) that comes into contact with the middle chamber S2 is supplied. And a lower radiating area α3 (corresponding to a first radiating area) to which radiating water (for example, about 28 ° C.) that comes into contact with the lower chamber S3 is supplied.
[0032]
The first cooling / heating unit β is provided with an upper boosting region β1 to which pressurized water (for example, about 58 ° C.) that comes into contact with the upper chamber S1 and a middle stage for which radiating water (for example, about 28 ° C.) to be brought into contact with the middle chamber S2. The heat radiation region β2 includes a lower cooling power output region β3 in which the cooling power water (for example, about 13 ° C.) that is in contact with the lower chamber S3 is output.
The second cooling output unit γ includes an upper radiating region γ1 (corresponding to a second radiating region) to which radiating water (for example, about 28 ° C.) that comes into contact with the upper chamber S1 and a cold output water (which corresponds to the second radiating region). (For example, about 13 ° C.) is output. Note that the temperature of the heat medium that comes into contact with the lower chamber S3 in the second cooling / heating output section γ is irrelevant, and that portion is referred to as an unquestionable area γ3.
[0033]
In other words, the group of the upper chambers S1 circulates through the heating zone α1 → the upper pressure boosting area β1 → the upper heat radiation area γ1 by the cell moving means (not shown). → Circulation in the middle cooling power output area γ2, and the group of lower chambers S3 circulates in the lower heat radiation area α3 → lower cooling power area β3 → non-contact area γ3.
[0034]
The group of the upper chambers S1 is covered with an upper vessel K1 (corresponding to one vessel), and the inside is divided into a heating area α1, an upper pressure stepping area β1, and an upper heat radiation area γ1. The group of the middle chambers S2 is covered with a middle vessel K2, and the inside thereof is divided into a middle boosted area α2, a middle heat radiation area β2, and a middle cooling output area γ2. Further, the group of lower chambers S3 is covered with a lower vessel K3, and the inside is divided into a lower heat radiation area α3, a lower cooling power output area β3, and a non-interest area γ3. Note that the middle container K2 and the lower container K3 correspond to the second container.
The upper container K1, the middle container K2, and the lower container K3 are containers K (for example, containers made of resin) provided continuously and connected, and the container K can be divided in the axial direction as shown in FIG. It is provided in.
[0035]
In the heat pump cycle 2 of this embodiment, in one cell S, when the upper chamber S1, the middle chamber S2, and the lower chamber S3 come into contact with a heat medium (heating water, radiating water, pressurized water, and cooling power output water), The contact start time of the heat medium that touches another chamber is provided to be shifted from the contact start time of the heat medium that touches another chamber.
The contact start timing of the heat medium in this embodiment will be described with reference to FIGS. 8 and 9, a solid line indicates a change in temperature and pressure in the upper chamber S1, a two-dot chain line indicates a change in temperature and pressure in the middle chamber S2, and a broken line indicates the temperature and pressure in the lower chamber S3. Indicates a change.
[0036]
When one cell S proceeds to the hydrogen drive unit α, the contact start time (αc in the figure) of the lower chamber S3 to contact the facility water is later than the contact start time (αa in the figure) of the upper chamber S1 to contact the heated water. Is provided. In this embodiment, the contact start time (αb in the figure) of the middle chamber S2 contacting the pressurized water is set at the same time as the contact start time (αa in the figure) of the upper chamber S1 contacting the heated water.
[0037]
When one cell S proceeds to the first cold output unit β, the contact start time (βc in the figure) of the lower chamber S3 comes in contact with the cold output water in comparison with the contact start time of the middle chamber S2 in the facility water (βb in the figure). ) Is provided late. In this embodiment, the contact start time of the upper chamber S1 in contact with the pressurized water (βa in the figure) is set at the same time as the contact start time of the middle chamber S2 in contact with the facility water (βb in the figure).
When one cell S proceeds to the second cold output section γ, the contact start time (γb in the figure) of the middle chamber S2 contacts the cold output water rather than the contact start time (γa in the figure) of the upper chamber S1 in contact with the facility water. ) Is provided late.
[0038]
As described above, the means for shifting the contact start time of the heat medium is implemented by adjusting the position or the thickness of the partition wall in the container K to which each heat medium is supplied.
Specifically, as shown in FIG. 2, the upper vessel K1 includes partition walls K1a, K1b, and K1c that partition a heating zone α1, an upper boost zone β1, and an upper heat radiation zone γ1, and the middle vessel K2 has a middle booster. A partition wall K2a, K2b, K2c that partitions the area α2, the middle heat radiation area β2, and the middle cooling power output area γ2, and the lower vessel K3 partitions the lower heat radiation area α3, the lower cooling power output area β3, and the non-interest area γ3. K3a, K3b, and K3c are provided.
[0039]
The partition wall K3a extends along the direction of movement of the cell S more than the partition walls K1a and K2a so that the lower chamber S3 enters later than the upper chamber S1 and the middle chamber S2 when the hydrogen drive unit α enters. It is provided at a shifted position (or the partition wall K3a is provided thick in the moving direction of the cell S).
Further, the partition wall K3b is moved more in the moving direction of the cell S than the partition walls K1b and K2b so that the lower chamber S3 enters later than the upper chamber S1 and the middle chamber S2 when the first cooling / heating output section β enters. (Or the partition wall K3b is provided thick in the moving direction of the cell S).
Further, the partition wall K2c is moved more in the moving direction of the cell S than the partition walls K1c and K3c so that the middle chamber S2 enters later than the upper chamber S1 and the lower chamber S3 when the second cooling / heating output section γ enters. (Or the partition wall K2c is provided thicker in the moving direction of the cell S).
[0040]
(Description of other components in heat pump cycle 2)
Reference numeral 9 shown in FIG. 3 denotes a pressurized water circulation path for circulating pressurized water in the upper pressure step-up region β1 and the middle pressure step-up region α2, and pressurized water is circulated by a pressurized water circulation pump P1 ′ provided on the way. The pressurized water uses water whose temperature is increased by heat transfer from the upper chamber S1 and the upper vessel K1 whose temperature is increased in the heating zone α1, and is used during the operation of the heat pump cycle 2. The temperature is, for example, about 58 ° C., and the temperature of the pressurized water in the middle step-up region α2 is, for example, about 56 ° C.
[0041]
(Description of combustion device 3)
The combustion device 3 according to the present embodiment uses a gas combustion device that burns gas as a fuel to generate heat and heats heated water by the generated heat. The gas burner 10 performs gas combustion, and the gas burner 10 A gas supply circuit 11 provided with a gas amount control valve 21 and a gas on-off valve 22 for supplying gas to the fuel gas 10, a combustion fan 12 for supplying air for combustion to the gas burner 10, and a heat exchange between heat of combustion of gas and heated water. And a heat exchanger 13 and the like.
Then, the heating water is heated to, for example, about 80 ° C. by the heat obtained by the gas combustion of the gas burner 10, and the heated heating water is supplied to the heating zone α1 via the heating water circulation path 14 having the heating water circulation pump P1. Is what you do.
Note that the heated water circulation pump P1 of this embodiment is a tandem pump driven by a motor that also serves to drive the pressurized water circulation pump P1 '. For this reason, when the heating water is supplied from the combustion device 3 to the heat pump cycle 2, the pressurized water is also provided so as to circulate.
[0042]
(Description of indoor air conditioner 5)
The indoor air conditioner 5 is disposed indoors as described above, and internally exchanges heat between the indoor heat exchanger 15 and the cold output water supplied to the indoor heat exchanger 15 and the indoor air. And an indoor fan 16 for blowing out the air after the heat exchange into the room. The indoor heat exchanger 15 is connected to a cold output water circulation passage 17 for circulating the cold output water supplied from the lower-stage cold output region β3 and the middle-stage cold output region γ2. (Inside) is provided a cold output water pump P2 for circulating the cold output water.
[0043]
(Explanation of the facility water cooling means 4)
The facility water cooling means 4 is an evaporative cooling tower, and the facility water cooled by the facility water cooling means 4 is supplied to the facility water circulation path 18 provided with the facility water circulation pump P3 by the lower heat radiation area α3 and the middle heat radiation area β2. , Is supplied to the upper heat radiation area γ1.
The facility water cooling means 4 allows the facility water passing through the lower heat radiation area α3, the middle heat radiation area β2, and the upper heat radiation area γ1 to flow from above to below, exchange heat with outside air while flowing, and release heat. During the evaporation, a part of the water is evaporated to remove vaporization heat from the facility water flowing at the time of evaporation, thereby cooling the facility water flowing. The radiating water cooling means 4 includes a radiating fan (not shown), and is provided so as to promote evaporation and cooling of the radiating water by an air flow generated by the radiating fan.
In this embodiment, an evaporative cooling tower is shown as the facility water cooling means 4, but a closed type cooling means in which facility water (heat medium for heat release) exchanges heat without contacting air may be used. good.
[0044]
Here, the above-described heated water circulation path 14, cold heat output water circulation path 17, and facility water circulation path 18 are provided with cisterns T1, T2, and T3, respectively, and the water levels in the cisterns T1, T2, and T3 are reduced to a predetermined water level or less. Then, the water supply valves T4, T5, T6 provided respectively are opened to supply tap water supplied from the water supply pipe 19 into the cisterns T1, T2, T3.
A drain pan P is provided below the heat pump cycle 2, and is provided so that drain water generated in the heat pump cycle 2 is drained from the drain pipe 20. The water overflowing from the facility water cooling means 4 is also drained from the drain pipe 20.
[0045]
(Description of control device 6)
The control device 6 responds to an operation instruction from a controller (not shown) provided in the indoor air conditioner 5 or an input signal of each of a plurality of sensors provided to the above-described heated water circulation pump P1 (pressurized water circulation pump P1 ′). , A cooling / heat output water pump P2, a facility water circulation pump P3, water supply valves T4, T5, T6, a facility fan such as a facility water cooling means 4, and a facility function of the combustion device 3 (combustion fan 12, gas amount control). It controls the valve 21, the gas on-off valve 22, an ignition device (not shown), and gives an instruction to the indoor air conditioner 5 to operate the indoor fan 16.
[0046]
(Operation explanation of cooling operation)
The operation of the cooling operation by the cooling device 1 will be described with reference to a PT refrigeration cycle diagram in FIG. 7, a graph showing a temperature change in FIG. 8, and a graph showing a pressure change in FIG. When the cooling operation is instructed by the controller of the indoor air conditioner 5, the control device 6 causes the combustion device 3, the cell moving means, the radiating fan and the heated water circulating pump P1 (pressurized water circulating pump P1 '), the cooling output water pump P2, and the heat radiation. The water circulation pump P3 operates, and the indoor fan 16 of the indoor air conditioner 5 for which cooling is instructed is turned on.
[0047]
The plurality of cells S rotate slowly and continuously by the cell moving means. Thereby, the plurality of cells S move in the order of the hydrogen driving unit α → the first cooling / heating output unit β → the second cooling / heating output unit γ.
In other words, each upper chamber S1 moves in the order of the heating zone α1, the upper boost zone β1, and the upper heat dissipation zone γ1, and each middle chamber S2 moves in the order of the middle boost zone α2, the middle heat dissipation zone β2, and the middle cooling output zone γ2. Then, each lower chamber S3 moves in the order of the lower heat radiation area α3 → the lower cooling power output area β3 → the non-interest area γ3.
[0048]
In the cell S entering the hydrogen drive unit α, first, the upper chamber S1 and the middle chamber S2 come into contact with heated water and pressurized water (αa, αb in FIG. 8). When the upper chamber S1 comes into contact with the heated water (80 ° C.), the high-temperature alloy HM releases hydrogen, and the internal pressure increases (αa in FIG. 9). Further, when the middle chamber S2 comes into contact with the pressurized water, the pressure rises to a pressure at which the middle temperature alloy MM does not absorb hydrogen (αb in FIG. 9).
After the internal pressures of the upper chamber S1 and the middle chamber S2 increase, the lower chamber S3 comes into contact with facility water (28 ° C.) (αc in FIG. 8), and the low-temperature alloy LM starts to store hydrogen (FIG. 9). αc). At this time, since the internal pressure of the upper chamber S1 has already risen and the high-temperature alloy HM has released hydrogen, the low-temperature alloy LM absorbs hydrogen without being affected by the delay in hydrogen transfer due to the pressure loss of the high-temperature alloy HM. I do.
[0049]
As described above, the upper chamber S1 touches the heating water in the heating area α1, the middle chamber S2 touches the pressurized water in the middle boosting area α2, and the lower chamber S3 touches the facility water in the lower heat dissipation area α3. 80 ° C .: 1.0 MPa, the inside of the middle chamber S2 is 56 ° C .: 1.0 MPa, the inside of the lower chamber S3 is 28 ° C .: 0.9 MPa, and the high-temperature alloy HM in the upper chamber S1 releases hydrogen (FIG. 7). (1)), the low-temperature alloy LM in the lower chamber S3 absorbs hydrogen ((2) in FIG. 7). The middle chamber S2 is heated by the pressurized water and has a high internal pressure, and the middle temperature alloy MM does not occlude hydrogen.
Then, the cell S that has passed through the hydrogen driving unit α moves to the first cooling / heating output unit β.
[0050]
First, the upper chamber S1 and the middle chamber S2 of the cell S entering the first cooling / heating output section β contact the pressurized water and the facility water (βa, βb in FIG. 8). When the upper chamber S1 comes in contact with the pressurized water (58 ° C.), the pressure rises to a pressure at which the high-temperature alloy HM does not absorb hydrogen (βa in FIG. 9). When the middle chamber S2 comes into contact with the facility water (28 ° C.), the internal pressure decreases due to the hydrogen absorbing action of the intermediate temperature alloy MM (βb in FIG. 9).
After the internal pressure of the middle chamber S2 has dropped, the lower chamber S3 comes into contact with the cold output water (βc in FIG. 8), thereby promoting the release of hydrogen from the low-temperature alloy LM (βc in FIG. 9). In other words, when the lower chamber S3 comes into contact with the cold output water, the internal pressure of the middle chamber S2 has already dropped, so that the low-temperature alloy LM is not affected by the delay in hydrogen transfer due to the pressure loss of the intermediate alloy MM. Releases hydrogen.
[0051]
As described above, the upper chamber S1 touches the pressurized water in the upper boost area β1, the middle chamber S2 touches the facility water in the middle boost area β2, and the lower chamber S3 touches the cold output water in the lower cool output area β3. 58 ° C .: 0.5 MPa in the upper chamber S 1, 28 ° C .: 0.4 MPa in the middle chamber S 2, 13 ° C .: 0.5 MPa in the lower chamber S 3, and the low-temperature alloy LM in the lower chamber S 3 releases hydrogen ( (3 in FIG. 7), the intermediate temperature alloy MM in the middle chamber S2 absorbs hydrogen ((4) in FIG. 7). When the low-temperature alloy LM in the lower chamber S3 releases hydrogen, an endothermic action is generated, and heat is taken from the cold output water that contacts the lower chamber S3. As a result, the temperature of the cooling output water in the lower cooling output region β3 decreases (for example, 13 ° C.). The upper chamber S1 is heated by the pressurized water and has a high internal pressure, and the high-temperature alloy HM does not store hydrogen.
Then, the cell S that has passed through the first cooling output unit β moves to the second cooling output unit γ.
[0052]
First, the upper chamber S1 of the cell S entering the second cooling / heating output section γ comes into contact with facility water (γa in FIG. 8). When the upper chamber S1 comes into contact with the facility water (28 ° C.), the internal pressure decreases due to the hydrogen absorbing action of the high-temperature alloy HM (γa in FIG. 9).
After the internal pressure of the upper chamber S1 has dropped, the middle chamber S2 comes into contact with the cold output water (γb in FIG. 8), thereby promoting the release of hydrogen from the intermediate temperature alloy MM (γb in FIG. 9). In other words, when the middle chamber S2 comes into contact with the cold output water, the internal pressure of the upper chamber S1 has already dropped, so that the medium temperature alloy MM is not affected by the delay in hydrogen transfer due to the pressure loss of the high temperature alloy HM. Releases hydrogen.
[0053]
As described above, by contacting the upper chamber S1 with the facility water in the upper heat radiation area γ1, the upper chamber S1 has a temperature of 28 ° C .: 0.1 MPa, the middle chamber S2 has a temperature of 13 ° C .: 0.2 MPa, and the lower chamber S3 has no problem. In this state, the middle temperature alloy MM in the middle chamber S2 releases hydrogen (5 in FIG. 7), and the high temperature alloy HM in the upper chamber S1 absorbs hydrogen (6 in FIG. 7). When the middle temperature alloy MM in the middle chamber S2 releases hydrogen, an endothermic action is generated, and heat is taken from the cold output water in contact with the middle chamber S2. As a result, the temperature of the cooling output water in the middle cooling output region γ2 decreases (for example, 13 ° C.). The temperature of the lower chamber S3 is irrelevant, and the low-temperature alloy LM in the lower chamber S3 does not store hydrogen.
Then, the cell S that has passed through the second cooling output unit γ moves to the hydrogen driving unit α.
[0054]
The low-temperature cold output water whose heat has been deprived in the lower-stage cold output region β3 and the middle-stage cold output region γ2 of the heat pump cycle 2 is supplied to the indoor heat exchanger 15 of the indoor air conditioner 5 via the cold output water circulation path 17. Then, heat is exchanged with the air blown into the room to cool the room.
[0055]
[Effects of the embodiment]
As shown in the above operation, in the cooling device 1 of the present embodiment, in one cell S, the upper chamber S1, the middle chamber S2, and the lower chamber S3 have the heat medium (heating water, facility water, pressurized water, cooling output). when touching the water), the contact start time of the heat medium to touch the certain room, by shifting the the contact start timing of the heat medium to touch the other room, without opening and closing the hydrogen passage S4, when hydrogen transfer By promoting the movement of hydrogen, it is possible to suppress a problem that the movement of hydrogen is delayed and the cooling efficiency is reduced, thereby improving the cooling efficiency of the cooling device 1.
In addition, since a plurality of cells S are used in which the upper chamber S1, the middle chamber S2, and the lower chamber S3 communicate with each other via the hydrogen passage S4, the pressure loss during the transfer of hydrogen is smaller than that of the shell and tube type heat exchanger. It can be suppressed, and the time until the pressure difference becomes constant (that is, the shifting time) can be shortened, and the cooling efficiency can be improved.
[0056]
The cooling device 1 of the present embodiment does not exchange heat with the hydrogen storage alloy by switching the type of the heat medium in contact with the hydrogen storage alloy as in the prior art, but the cell moving means moves a plurality of cells S. As a result, the hydrogen storage alloy itself moves to change the type of the heat medium (heating water, facility water, pressurized water, and cold output water), so that a switching valve for switching the type of the heat medium in the heat pump cycle 2 is unnecessary. Become. Further, since the upper chamber S1, the middle chamber S2, and the lower chamber S3 are all connected only by the hydrogen passage S4, there is no need to provide an opening / closing valve for the hydrogen passage S4.
As described above, the cooling device 1 of the present embodiment does not require the switching valve that frequently switches the heat medium in the heat pump cycle 2, so that the failure probability is reduced as compared with the related art, and as a result, long-term reliability is improved. improves.
[0057]
The cooling device 1 to which the present invention is applied uses a plurality of cells S in which the upper chamber S1, the middle chamber S2, and the lower chamber S3 each containing a hydrogen storage alloy are communicated with each other through a hydrogen passage S4. As compared with the heat exchanger, the heat transfer of the portion not involved in the heat exchange is reduced, the heat loss can be reduced, and the pressure loss during the transfer of hydrogen is suppressed to be small. As a result, the cooling efficiency of the heat pump cycle 2 is improved, and the cooling efficiency is improved. Is improved.
[0058]
The heat pump cycle 2 of the cooling device 1 to which the present invention is applied is not a heat and heat exchanger of the conventional shell and tube type, but a plurality of cells S assembled and housed in one container K. It is. For this reason, the size of the heat pump cycle 2 of the present embodiment can be significantly reduced as compared with the conventional heat pump cycle using a plurality of shell and tube type heat exchangers. The machine 7 can be downsized.
[0059]
[Second embodiment]
Next, a second embodiment in which the hydrogen storage cooling device of the present invention is applied to a cooling and heating device will be described. FIG. 10 is a schematic configuration diagram of a cooling and heating device to which the present invention is applied.
The cooling / heating device 30 of the present embodiment guides the heated water heated by the combustion device 3 to the indoor heat exchanger 15 of the indoor air conditioner 5 during the heating operation in addition to the cooling operation described in the above embodiment. For heating the room, the heating water circulation path 14 and the cooling / heating output water circulation path 17 shown in the first embodiment are connected to each other, and three connection valves V1, V2, V3 (for cooling and (A switching valve for heating).
In addition, in addition to the indoor air conditioner 5, it may be connected to a floor heating mat, a bathroom drier, or the like, and provided so as to perform floor heating, bathroom heating, or the like by supplying heating water.
[0060]
(Modification)
In the above embodiment, the example in which the contact start time of the heat medium is shifted every time each chamber of the cell S enters the next heat medium region, however, only a part may be shifted. That is, for example, only the hydrogen driving unit α may be shifted, only the first cooling output unit β may be shifted, or only the second cooling output unit γ may be shifted.
[0061]
In the above-described first and second embodiments, the upper chamber S1, the middle chamber S2, and the lower chamber S3 have been described as an example in accordance with the upper and lower sides of the drawing in order to facilitate the description. It may be arranged in other directions, such as turning sideways or turning over. Further, the arrangement of the upper chamber S1, the middle chamber S2, and the lower chamber S3 may be interchanged. Further, the moving direction of the cell S may be reversed. In such a case, of course, the arrangement positions of the respective heat carriers that come into contact with the respective chambers are also changed so that the heat pump cycle is established.
[0062]
In the above embodiment, an example is shown in which a heating medium (pressurized water in the embodiment) whose temperature has been raised by cooling the upper chamber S1 whose temperature has been increased in the heating zone α1 has been used as the heating medium for increasing pressure. A heat medium whose temperature has been raised by a means (for example, a temperature rise by a combustion device, a temperature rise by an electric heater, a temperature rise using exhaust heat, and the like) may be used.
In the above embodiment, an example in which a two-stage cycle is used as an example of the heat pump cycle 2 has been described. However, the heat pump cycle 2 may be used in a one-stage cycle, or the second chamber may be divided into three or more to form a three-stage cycle. The above cycle may be used.
[0063]
In the above embodiment, a multi-air conditioner in which a plurality of indoor air conditioners 5 can be connected to one outdoor unit 7 has been described, but the present invention is applied to an air conditioner in which one indoor air conditioner 5 is connected to one outdoor unit 7. May be applied.
In the above-described embodiment, an example in which the room is cooled with the heat medium for cooling output (cooling water in the embodiment) obtained by the heat pump cycle 2 has been described. For example, the present invention may be used as another cooling device.
[0064]
In the above embodiment, an example in which one heat pump unit (a unit in which a plurality of cells S are accommodated in one container K) is used. It may be used for a cooling device requiring a large cooling capacity, such as an air conditioning system for a vehicle.
[0065]
In the above embodiment, a gas combustion device for burning gas is used as a heating means for heating a heat medium for heating (heating water in the embodiment), but other combustion devices such as an oil combustion device for burning oil are used. An apparatus may be used, or other heating means such as a heating means for heating a heating medium for heating by exhaust heat of an internal combustion engine, steam from a boiler, or a heating means using an electric heater may be used. When utilizing the exhaust heat of the internal combustion engine, it can also be used for vehicles.
[0066]
In the above embodiment, tap water is used as an example of each heat medium, but another liquid heat medium such as antifreeze or oil may be used, or a gas heat medium such as air may be used.
In the above embodiment, an example in which rotated continuously by the cell moving means multiple cells S, may be intermittently rotated moving the cell S.
[Brief description of the drawings]
FIG. 1 is a diagram illustrating the operation of a heat pump cycle (first embodiment).
FIG. 2 is a sectional view of each part of a container for accommodating a cell assembly (first embodiment).
FIG. 3 is a schematic configuration diagram of a cooling device (first embodiment).
FIG. 4 is a perspective view of a cell (first embodiment).
FIG. 5 is a perspective view showing an arrangement state of a plurality of cells (first embodiment).
FIG. 6 is a perspective view of a container (first embodiment).
FIG. 7 is a PT refrigeration cycle diagram (first embodiment).
FIG. 8 is a graph showing a temperature change in each room (first embodiment).
FIG. 9 is a graph showing a pressure change in each chamber (first embodiment).
FIG. 10 is a schematic configuration diagram of a cooling and heating device (second embodiment).
FIG. 11 is a schematic configuration diagram of a cooling device (conventional example).
[Explanation of symbols]
HM high temperature alloy (hydrogen storage alloy)
MM Medium temperature alloy (hydrogen storage alloy)
LM Low temperature alloy (hydrogen storage alloy)
S cell S1 Upper chamber (first chamber)
S2 Middle room (2nd room)
S3 Lower room (2nd room)
S4 Hydrogen passage α Hydrogen driving part α1 Heating area α3 Lower heat radiation area (first heat radiation area)
γ 2nd cooling output section (cooling output section)
γ1 upper heat radiation area (second heat radiation area)
γ2 middle stage cooling output area (cooling output area)
K1 Upper container (first container)
K2 Middle container (second container)
K3 Lower container (second container)

Claims

In the hydrogen storage type cooling device using the heat absorption of the hydrogen storage alloy when releasing hydrogen,
A plurality of cells including a first chamber in which the hydrogen storage alloy is sealed, a second chamber in communication with the first chamber through the hydrogen passage, and having the hydrogen storage alloy sealed therein;
A first heat radiating area provided with a heat medium for heating provided in contact with the first chamber and provided with a heat medium for heat radiating provided in contact with the second chamber; A hydrogen drive unit comprising:
A second heat radiation area provided with a heat medium for heat radiation provided so as to be capable of contacting the first chamber, and a cold heat provided with a heat medium for heat output provided so as to be able to contact the second chamber; A cooling output unit having an output area,
Cell moving means for repeatedly moving the plurality of cells to the hydrogen drive unit and the cold heat output unit,
When the first chamber contacts the heating medium for heating in the hydrogen driving unit, and the second chamber contacts the heating medium for heat radiation, the first chamber comes into contact with the heating medium for heating, more than the contact start time. The contact start timing at which the second chamber comes into contact with the heat medium for heat radiation is provided late,
When the first chamber is in contact with the heat medium for heat dissipation in the cold heat output section and the second chamber is in contact with the heat medium for heat output, the first chamber is in contact with the heat medium for heat dissipation, which is shorter than the contact start time. the second chamber is shall have provided slow contact start time to touch the heat medium for cold output,
The plurality of cells are arranged such that the first chamber and the second chamber each have a radial shape,
The cell moving means radially drives the plurality of cells,
The heating area and the second heat radiation area are partitioned in a first container that covers the group of the first chamber,
The first heat radiation area and the cold heat output area are partitioned in a second container covering the group of the second chamber;
The difference between the contact start time of the heat medium that touches the first chamber and the contact start time of the heat medium that touches the second chamber is the difference between the first heat radiation area and the cold heat output area. A hydrogen-absorbing-type cooling device, which is provided depending on the position or thickness of a partition wall .

The hydrogen storage type cooling device according to claim 1 ,
The second chamber is divided into a plurality of sections through a hydrogen passage, one of the divided second chambers is brought into contact with a heat medium for heat radiation, and the other of the divided second chambers is contacted with a heat medium for cold heat output. And hydrogen is transferred from the other second chamber to the one second chamber so as to obtain a cooling output,
When the one second chamber is in contact with the heat medium for heat dissipation and the other second chamber is in contact with the heat medium for cold heat output, the contact start time when the one second chamber is in contact with the heat medium for heat dissipation is Also, the hydrogen-absorbing cooling device is characterized in that the contact start time of the other second chamber in contact with the heat medium for cooling output is set later.

The hydrogen-absorbing cooling device according to claim 1 or 2 ,
The first chamber and the second chamber each have a flat shape, and one surface is curved in a convex shape, and the other surface facing one surface is provided in a concave shape. Hydrogen storage cooling device.